US11286919B2 - Variable displacement swash plate type compressor - Google Patents
Variable displacement swash plate type compressor Download PDFInfo
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- US11286919B2 US11286919B2 US16/979,273 US201916979273A US11286919B2 US 11286919 B2 US11286919 B2 US 11286919B2 US 201916979273 A US201916979273 A US 201916979273A US 11286919 B2 US11286919 B2 US 11286919B2
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- orifice hole
- cylindrical portion
- pressure
- chamber
- crankcase
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/109—Lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1809—Controlled pressure
- F04B2027/1813—Crankcase pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1822—Valve-controlled fluid connection
- F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1822—Valve-controlled fluid connection
- F04B2027/1831—Valve-controlled fluid connection between crankcase and suction chamber
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1886—Open (not controlling) fluid passage
- F04B2027/1895—Open (not controlling) fluid passage between crankcase and suction chamber
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1081—Casings, housings
Definitions
- the present disclosure relates to a variable displacement swash plate type compressor and more particularly to a variable displacement swash plate type compressor which controls the pressure of a crankcase equipped with a swash plate and adjusts an inclination angle of the swash plate.
- a compressor functioning to compress the refrigerant in a vehicle cooling system has been developed in various types.
- a configuration for compressing the refrigerant includes a reciprocating type for compressing the refrigerant while performing a reciprocating motion and a rotation type for compressing the refrigerant while performing a rotational motion.
- the reciprocating type includes a crank type for transmitting a driving force of a driving source to a plurality of pistons by using a crank, a swash plate type for transmitting a driving force of a driving source to a rotating shaft with the swash plate installed therein, and a wobble plate type using a wobble plate.
- the rotation type includes a vane rotary type using a rotating shaft and a vane, and a scroll type using an orbiting scroll and a fixed scroll.
- the swash plate type compressor has a swash plate rotating together with the rotating shaft and compresses the refrigerant by reciprocating a piston.
- the swash plate type compressor is formed in a so-called variable displacement type which controls the refrigerant discharge amount by controlling the stroke of the piston through the adjustment of the inclination angle of the swash plate.
- FIG. 1 is a perspective view showing a conventional variable displacement swash plate type compressor of which a portion is cut away to show the internal structure thereof.
- the conventional variable displacement swash plate type compressor includes: a casing 100 which has a bore 114 , a suction chamber S 1 , a discharge chamber S 3 , and a crankcase S 4 , a rotating shaft 210 which is supported rotatably on the casing 100 , a swash plate 220 which is rotated within the crankcase S 4 in conjunction with the rotating shaft 210 , a piston 230 which reciprocates within the bore 114 in conjunction with the swash plate 220 and forms, together with the bore 114 , a compression chamber, a valve mechanism 300 which communicates and shields the suction chamber S 1 and the discharge chamber S 3 with and from the compression chamber, and an inclination adjustment mechanism 400 which adjusts an inclination angle of the swash plate 220 with respect to the rotating shaft 210 .
- the inclination adjustment mechanism 400 includes a first flow path 430 which communicates the discharge chamber S 3 with the crankcase S 4 , and a second flow path 450 which communicates the crankcase S 4 with the suction chamber S 1 .
- a pressure control valve (not shown) that opens and closes the first flow path 430 is formed on the first flow path 430 .
- An orifice hole 460 that decompresses a fluid passing through the second flow path 450 is formed in the second flow path 450 .
- variable displacement swash plate type compressor when the power is transmitted from a driving source (e.g., an engine of a vehicle) (not shown) to the rotating shaft 210 , the rotating shaft 210 and the swash plate 220 rotate together.
- a driving source e.g., an engine of a vehicle
- the piston 230 reciprocates within the bore 114 by converting the rotational motion of the swash plate 220 into a linear motion.
- the compression chamber communicates with the suction chamber S 1 by the valve mechanism 300 and is shielded from the discharge chamber S 3 , so that the refrigerant in the suction chamber S 1 is sucked into the compression chamber.
- the compression chamber is shielded from the suction chamber S 1 and the discharge chamber S 3 by the valve mechanism 300 , and the refrigerant in the compression chamber is compressed.
- the compression chamber is shielded from the suction chamber S 1 by the valve mechanism 300 and communicates with the discharge chamber S 3 , so that the refrigerant compressed in the compression chamber is discharged to the discharge chamber S 3 .
- the refrigerant discharge amount of the conventional variable displacement swash plate type compressor is controlled as follow.
- the compressor when the compressor is stopped, the compressor is set to a minimum mode in which the refrigerant discharge amount is minimum. That is, the swash plate 220 is disposed close to perpendicular to the rotating shaft 210 , and an inclination angle of the swash plate 220 is close to zero.
- the inclination angle of the swash plate 220 is measured as an angle between the rotating shaft 210 of the swash plate 220 and a normal of the swash plate 220 , based on the center of rotation of the swash plate 220 .
- the compressor is adjusted to a maximum mode in which the refrigerant discharge amount is maximum. That is, the first flow path 430 is closed by the pressure control valve (not shown), and the refrigerant in the crankcase S 4 flows into the suction chamber S 1 through the second flow path 450 , so that the pressure in the crankcase S 4 is reduced to the level of the suction pressure (the pressure in the suction chamber S 1 ). Accordingly, the pressure in the crankcase S 4 applied to the piston 230 is reduced to the minimum degree, and the stroke of the piston 230 is increased to the maximum degree. Then, the inclination angle of the swash plate 220 is increased to the maximum degree, and the refrigerant discharge amount is increased to the maximum degree.
- the piston 230 forms the inclination angle of the swash plate as a moment difference due to a differential pressure obtained by subtracting the pressure in the crankcase S 4 from the pressure in the compression chamber mainly applied to the piston 230 .
- the lower the pressure in the crankcase S 4 the more the inclination angle of the swash plate 220 increases and the more the stroke of the piston 230 increases and the more the refrigerant discharge amount increases.
- the greater the pressure in the crankcase S 4 the more the inclination angle of the swash plate 220 decreases and the more the stroke of the piston 230 decreases and the more the refrigerant discharge amount decreases.
- the opening amount of the first flow path 430 is controlled by the pressure control valve (not shown), so that the pressure in the crankcase S 4 is controlled. Accordingly, the pressure in the crankcase S 4 applied to the piston 230 is controlled, so that the stroke of the piston 230 is adjusted, the inclination angle of the swash plate 220 is adjusted, and the refrigerant discharge amount is adjusted.
- the first flow path 430 is opened by the pressure control valve (not shown), and the opening amount of the first flow path 430 is increased by the pressure control valve (not shown), so that the pressure in the crankcase S 4 is increased.
- the amount of the refrigerant which is introduced from the discharge chamber S 3 into the suction chamber S 1 through the first flow path 430 is greater than the amount of the refrigerant which is discharged from the crankcase S 4 to the suction chamber S 1 through the second flow path 450 , so that the pressure in the crankcase S 4 is increased. Accordingly, the pressure in the crankcase S 4 applied to the piston 230 is increased, so that the stroke of the piston 230 is reduced, the inclination angle of the swash plate 220 is reduced, and the refrigerant discharge amount is reduced.
- the first flow path 430 is opened by the pressure control valve (not shown), and the opening amount of the first flow path 430 is decreased by the pressure control valve (not shown), so that the pressure in the crankcase S 4 is decreased.
- the refrigerant in the discharge chamber S 3 is introduced into the suction chamber S 1 through the first flow path 430
- the amount of the refrigerant which is discharged from the crankcase S 4 into the suction chamber S 1 through the second flow path 450 is greater than the amount of the refrigerant which is introduced from the discharge chamber S 3 into the suction chamber S 1 through the first flow path 430 , so that the pressure in the crankcase S 4 is decreased.
- the pressure in the crankcase S 4 applied to the piston 230 is decreased, so that the stroke of the piston 230 is increased, the inclination angle of the swash plate 220 is increased, and the refrigerant discharge amount is increased.
- the crankcase S 4 in order to increase the refrigerant discharge amount through the reduction of the pressure in the crankcase S 4 , the crankcase S 4 is in communication with the suction chamber S 1 through the second flow path 450 .
- the cross-sectional area of the orifice hole 460 of the second flow path 450 is formed as large as possible. That is, the refrigerant in the crankcase S 4 is quickly discharged to the suction chamber S 1 , so that the pressure in the crankcase S 4 is rapidly reduced, the stroke of the piston 230 is rapidly increased, and the inclination angle of the swash plate 220 is rapidly increased.
- the orifice hole 460 is formed as a fixed orifice hole, and the cross-sectional area of the orifice hole 460 is formed maximally within a range in which the refrigerant passing through the second flow path 450 is sufficiently decompressed.
- the cross-sectional area of the orifice hole 460 is formed as large as possible, a large amount of the refrigerant leaks from the crankcase S 4 to the suction chamber S 1 .
- the amount of the refrigerant which is introduced from the discharge chamber S 3 into the crankcase S 4 through the first flow path 430 should be increased more than that of when the cross-sectional area of the orifice hole 460 is formed relatively small.
- the power input to the compressor must be increased such that the compressor compresses more refrigerant, and thus, the efficiency of the compressor is reduced.
- the conventional swash plate type compressor has a problem in that the time required to switch to the maximum mode is increased.
- the purpose of the present disclosure is to provide a variable displacement swash plate type compressor capable of achieving rapid control of the refrigerant discharge amount and the prevention of reduction in compressor efficiency at the same time.
- Another purpose of the present disclosure is to provide a variable displacement swash plate type compressor capable of reducing the time required to switch to the maximum mode.
- One embodiment is a variable displacement swash plate type compressor including: a casing which has a bore, a suction chamber, a discharge chamber, and a crankcase; a rotating shaft which is supported rotatably on the casing; a swash plate which is rotated within the crankcase in conjunction with the rotating shaft; a piston which reciprocates within the bore in conjunction with the swash plate and forms, together with the bore, a compression chamber; and an inclination adjustment mechanism which has a first flow path which communicates the discharge chamber with the crankcase and a second flow path which communicates the crankcase with the suction chamber, in order to adjust an inclination angle of the swash plate with respect to the rotating shaft.
- An orifice hole which decompresses a fluid passing through the second flow path is formed in the second flow path.
- An orifice control mechanism which controls an effective flow cross-sectional area of the orifice hole is formed on the second flow path.
- the orifice hole and the orifice control mechanism are formed such that when a differential pressure between a pressure in the crankcase and a pressure in the suction chamber is increased, the effective flow cross-sectional area changes from zero to a first area that is larger than zero and when the differential pressure is further increased, the effective flow cross-sectional area becomes a second area that is larger than zero and less than the first area.
- the orifice hole may include: a first orifice hole which is in communication with the crankcase; a third orifice hole which is in communication with the suction chamber; and a second orifice hole which is formed between the first orifice hole and the third orifice hole.
- the orifice control mechanism may include: a valve chamber which is in communication with the first orifice hole and the second orifice hole; and a valve core which reciprocates along the valve chamber and controls an opening amount of the first orifice hole, an opening amount of the second orifice hole, and an opening amount of the third orifice hole
- the orifice hole and the orifice control mechanism may be formed such that, when the differential pressure is less than a first pressure, the effective flow cross-sectional area becomes zero, when the differential pressure is greater than or equal to the first pressure and less than a second pressure, the effective flow cross-sectional area becomes the first area, and when the differential pressure is greater than or equal to the second pressure, the effective flow cross-sectional area becomes the second area.
- the valve chamber may include: a valve chamber inner circumferential surface which guides the reciprocating motion of the valve core; a valve chamber first front end surface which is located at one end side of the valve chamber inner circumferential surface; and a valve chamber second front end surface which is located at the other end side of the valve chamber inner circumferential surface.
- the first orifice hole may be in communication with the valve chamber at the valve chamber first front end surface.
- the second orifice hole 464 may be in communication with the valve chamber at the valve chamber second front end surface.
- the third orifice hole may be in communication with the second orifice hole at a position facing the valve chamber, so that the first orifice hole, the valve chamber, the second orifice hole, and the third orifice hole are formed sequentially according to a direction of the reciprocating motion of the valve core.
- the valve core may include: a first end which reciprocates within the valve chamber and controls the opening amount of the first orifice hole; and a second end which extends from the first end and reciprocates together with the first end, and controls the opening amounts of the second orifice hole and the third orifice hole
- the first end may include: a first cylindrical portion which comprises an outer circumferential surface facing the valve chamber inner circumferential surface, a bottom surface facing the second orifice hole, and an upper surface facing the third orifice hole; a second cylindrical portion which extends from the upper surface of the first cylindrical portion to the second orifice hole 464 side and forms a concentric circle with the first cylindrical portion; and a plurality of protrusions which are formed radially from the outer circumferential surface of the first cylindrical portion and the outer circumferential surface of the second cylindrical portion with respect to central axes of the first cylindrical portion and the second cylindrical portion.
- the second end may include a third cylindrical portion which further extends from the second cylindrical portion to the second orifice hole side and forms a concentric circle with the second cylindrical portion
- An outer diameter of the first cylindrical portion may be formed to be less than an outer diameter of the plurality of protrusions.
- An outer diameter of the second cylindrical portion may be formed to be less than the outer diameter of the first cylindrical portion.
- An outer diameter of the third cylindrical portion may be formed at an equal level to the outer diameter of the second cylindrical portion.
- An inner diameter of the valve chamber may be formed at an equal level to the outer diameter of the plurality of protrusions.
- An inner diameter of the first orifice hole may be formed to be less than the outer diameter of the first cylindrical portion.
- An inner diameter of the second orifice hole may be formed to be larger than the outer diameter of the third cylindrical portion and may be formed to be less than the outer diameter of the plurality of protrusions.
- An inner diameter of the third orifice hole may be formed to be larger than the outer diameter of the third cylindrical portion and may be formed to be less than the inner diameter of the second orifice hole.
- a length of the plurality of protrusions may be formed to be less than a length of the valve chamber.
- a length obtained by adding a length of the first cylindrical portion and a length of the second cylindrical portion may be formed at an equal level to the length of the plurality of protrusions.
- a length of the third cylindrical portion may be formed to be larger than a length of the second orifice hole and may be formed to be less than a length obtained by adding the length of the second orifice hole 464 and a length of the third orifice hole.
- a length obtained by adding the length of the plurality of protrusions and the length of the third cylindrical portion may be formed to be larger than the length of the valve chamber and may be formed to be less than a length obtained by adding the length of the valve chamber and the length of the second orifice hole.
- An area obtained by subtracting an area of the third cylindrical portion from a cross-sectional area of the second orifice hole may be formed as the first area.
- An area obtained by subtracting the area of the third cylindrical portion from a cross-sectional area of the third orifice hole may be formed as the second area.
- a cross-sectional area of the first orifice hole may be formed to be equal to or greater than the first area.
- An area obtained by subtracting an area of the first cylindrical portion and an area of the plurality of protrusions from a cross-sectional area of the valve chamber may be formed to be equal to or greater than the cross-sectional area of the first orifice hole.
- the orifice control mechanism may further include an elastic member which presses the valve core toward the valve chamber first front end surface.
- the casing may include: a cylinder block in which the bore is formed; a front housing which is coupled to one side of the cylinder block and in which the crankcase is formed; and a rear housing which is coupled to the other side of the cylinder block and in which the suction chamber and the discharge chamber are formed.
- a valve mechanism which communicates and shields the suction chamber and the discharge chamber with and from the compression chamber may be interposed between the cylinder block and the rear housing.
- the rear housing 130 may include a post portion 132 which extends from an inner wall surface of the rear housing 130 and is supported by the valve mechanism in order to prevent deformation of the rear housing 130 .
- the first orifice hole 462 may be formed in the valve mechanism.
- the valve chamber 472 , the second orifice hole 464 , and the third orifice hole 466 may be formed in the post portion
- the orifice hole and the orifice control mechanism may be formed such that the effective flow cross-sectional area becomes zero when the compressor is stopped.
- a variable displacement swash plate compressor includes: a casing which has a bore, a suction chamber, a discharge chamber, and a crankcase; a rotating shaft which is supported rotatably on the casing; a swash plate which is rotated within the crankcase in conjunction with the rotating shaft; a piston which reciprocates within the bore in conjunction with the swash plate and forms, together with the bore, a compression chamber; and an inclination adjustment mechanism which has a first flow path which communicates the discharge chamber with the crankcase and a second flow path which communicates the crankcase with the suction chamber, in order to adjust an inclination angle of the swash plate with respect to the rotating shaft.
- An orifice hole which decompresses a fluid passing through the second flow path is formed in the second flow path.
- An orifice control mechanism which controls an effective flow cross-sectional area of the orifice hole is formed on the second flow path.
- the orifice hole and the orifice control mechanism are formed such that when a differential pressure between a pressure in the crankcase and a pressure in the suction chamber is increased, the effective flow cross-sectional area changes from zero to a first area that is larger than zero and when the differential pressure is further increased, the effective flow cross-sectional area becomes a second area that is larger than zero and less than the first area.
- FIG. 1 is a perspective view showing a conventional variable displacement swash plate type compressor
- FIG. 2 is a cross-sectional view showing a second flow path in a variable displacement swash plate type compressor according to an embodiment of the present disclosure
- FIG. 3 is a perspective view of a valve core of FIG. 2 when viewed from one side;
- FIG. 4 is a perspective view of the valve core of FIG. 2 when viewed from the other side;
- FIG. 5 is an enlarged cross-sectional view of a part “I” of FIG. 2 and shows that a differential pressure is less than a first pressure
- FIG. 6 is an enlarged cross-sectional view of the part “I” of FIG. 2 and shows that the differential pressure is greater than or equal to the first pressure and less than a second pressure;
- FIG. 7 is an enlarged cross-sectional view of the part “I” of FIG. 2 and shows that the differential pressure is greater than or equal to the second pressure;
- FIG. 8 is a graph showing changes in an effective flow cross-sectional area of an orifice hole according to the differential pressure in the variable displacement swash plate type compressor of FIG. 2 ;
- FIG. 9 is a cross-sectional view showing the second flow path in a variable displacement swash plate type compressor according to another embodiment of the present disclosure.
- FIG. 10 is a graph showing changes in an effective flow cross-sectional area of the orifice hole according to the differential pressure in the variable displacement swash plate type compressor of FIG. 11 ;
- FIG. 11 is a graph showing changes in the effective flow cross-sectional area of the orifice hole according to the differential pressure in a variable displacement swash plate type compressor according to further another embodiment of the present disclosure.
- variable displacement swash plate type compressor according to the present disclosure will be described in detail with reference to the accompanying drawings.
- FIG. 2 is a cross-sectional view showing a second flow path in the variable displacement swash plate type compressor according to an embodiment of the present disclosure.
- FIG. 3 is a perspective view of a valve core of FIG. 2 when viewed from one side.
- FIG. 4 is a perspective view of the valve core of FIG. 2 when viewed from the other side.
- FIG. 5 is an enlarged cross-sectional view of a part “I” of FIG. 2 and shows that a differential pressure is less than a first pressure.
- FIG. 6 is an enlarged cross-sectional view of the part “I” of FIG. 2 and shows that the differential pressure is greater than or equal to the first pressure and less than a second pressure.
- FIG. 7 is an enlarged cross-sectional view of the part “I” of FIG. 2 and shows that the differential pressure is greater than or equal to the second pressure.
- FIG. 8 is a graph showing changes in an effective flow cross-sectional area of an orifice hole according to the differential pressure in the variable displacement swash plate
- FIGS. 2 to 7 make reference to FIG. 1 for convenience of description.
- variable displacement swash plate type compressor may include a casing 100 and a compression mechanism 200 which is provided within the casing 100 and compresses refrigerant.
- the casing 100 may include a cylinder block 110 in which the compression mechanism 200 is received, a front housing 120 which is coupled to a front side of the cylinder block 110 , and a rear housing 130 which is coupled to a rear side of the cylinder block 110 .
- a shaft receiving hole 112 into which a later-mentioned rotating shaft 210 is inserted is formed on the center side of the cylinder block 110 .
- a piston 230 to be described later is inserted into the outer circumferential portion of the cylinder block 110 , and a bore 114 which forms, together with the piston 230 , a compression chamber may be formed.
- the shaft receiving hole 112 may be formed in a cylindrical shape passing through the cylinder block 110 along the axial direction of the cylinder block 110 .
- the bore 114 may be formed in a cylindrical shape passing through the cylinder block 110 along the axial direction of the cylinder block 110 at a portion spaced apart outward in a radial direction of the cylinder block 110 from the shaft receiving hole 112 .
- n number of the bores 114 may be formed such that n number of the compression chambers are formed.
- the n number of bores 114 may be arranged along the circumferential direction of the cylinder block 110 around the shaft receiving hole 112 .
- the front housing 120 may be fastened to the cylinder block 110 on the opposite side of the rear housing 130 with respect to the cylinder block 110 .
- crankcase S 4 between the cylinder block 110 and the front housing 120 .
- a swash plate 220 to be described later may be received in the crankcase S 4 .
- the rear housing 130 may be fastened to the cylinder block 110 on the opposite side of the front housing 120 with respect to the cylinder block 110 .
- the rear housing 130 may be formed with a suction chamber S 1 in which the refrigerant to be introduced into the compression chamber is received and with a discharge chamber S 3 in which the refrigerant discharged from the compression chamber is received.
- the suction chamber S 1 may be in communication with a refrigerant suction pipe (not shown) that guides the refrigerant to be compressed to the interior of the casing 100 .
- the discharge chamber S 3 may be in communication with a refrigerant discharge pipe (not shown) that guides the compressed refrigerant to the outside of the casing 100 .
- the compressor mechanism 200 may be formed to suck the refrigerant from the suction chamber S 1 into the compression chamber, to compress the sucked refrigerant in the compression chamber, and to discharge the compressed refrigerant from the compression chamber to the discharge chamber S 3 .
- the compression mechanism 200 may include the rotating shaft 210 which is rotatably supported on the casing 100 and is rotated by receiving a rotational force from a driving source (for example, an engine of a vehicle) (not shown), a swash plate 220 which is rotated within the crankcase S 4 in conjunction with the rotating shaft 210 , and a piston 230 which reciprocates within the bore 114 in conjunction with the swash plate 220 .
- a driving source for example, an engine of a vehicle
- a swash plate 220 which is rotated within the crankcase S 4 in conjunction with the rotating shaft 210
- a piston 230 which reciprocates within the bore 114 in conjunction with the swash plate 220 .
- the rotating shaft 210 may be formed in a cylindrical shape extending in one direction.
- one end of the rotating shaft 210 may be inserted into the cylinder block 110 (more precisely, the shaft receiving hole 112 ) and rotatably supported.
- the other end of the rotating shaft 210 may pass through the front housing 120 and protrude to the outside of the casing 100 and may be connected to the driving source (not shown).
- the swash plate 220 may be formed in a disk shape and may be obliquely fastened to the rotating shaft 210 in the crankcase S 4 .
- the swash plate 220 is fastened to the rotating shaft 210 such that the inclination angle of the swash plate 220 is variable. This will be described later.
- N number of the pistons 230 are provided in corresponding to the bore 114 .
- Each of the pistons 230 may be formed to be in conjunction with the swash plate 220 and reciprocate in the bore 114 .
- the piston 230 may include one end which is inserted into the bore 114 and the other end which extends from the one end to the opposite side of the bore 114 and is connected to the swash plate 220 in the crankcase S 4 .
- variable displacement swash plate type compressor may further include a valve mechanism 300 which communicates and shields the suction chamber S 1 and the discharge chamber S 3 with and from the compression chamber.
- the valve mechanism 300 may include a valve plate interposed between the cylinder block 110 and the rear housing 130 , a suction lid interposed between the cylinder block 110 and the valve plate, and a discharge lid interposed between the valve plate and the rear housings 130 .
- the valve plate may be formed approximately in a disk shape and may include a suction port through which the refrigerant to be compressed passes and a discharge port through which the compressed refrigerant passes.
- N number of the suction ports may be formed in correspondence to the compression chamber, and the n number of suction ports may be arranged along the circumferential direction of the valve plate.
- N number of the discharge ports may be also formed in correspondence to the compression chamber, and the n number of discharge ports may be arranged along the circumferential direction of the valve plate from the central point of the valve plate with respect to the suction port.
- the suction lid may be formed approximately in a disk shape and may include a suction valve which opens and closes the suction port and a discharge hole which communicates the compression chamber with the discharge port.
- the suction valve may be formed in a cantilevered shape, and n number of the suction valves may be formed in correspondence to the compression chamber and the suction port. The n number of suction valves may be arranged along the circumferential direction of the suction lid.
- the discharge hole may be formed to pass through the suction lid from the base of the suction valve, and n number of the discharge holes may be formed in correspondence to the compression chamber and the discharge port.
- the n number of discharge holes may be arranged along the circumferential direction of the suction lid.
- the discharge lid may be formed approximately in a disk shape and may include a discharge valve which opens and closes the discharge port and a suction hole which communicates the suction chamber S 1 with the suction port.
- the discharge valve may be formed in a cantilevered shape, and n number of the discharge valves may be formed in correspondence to the compression chamber and the discharge port. The n number of discharge valves may be arranged along the circumferential direction of the discharge lid.
- the suction hole may be formed to pass through the discharge lid from the base of the discharge valve, and n number of the suction holes may be formed in correspondence to the compression chamber and the suction port.
- the n number of suction holes may be arranged along the circumferential direction of the discharge lid.
- the swash plate type compressor according to the embodiment of the present disclosure may further include a discharge gasket interposed between the discharge lid and the rear housing 130 .
- variable displacement swash plate type compressor may further include an inclination adjustment mechanism 400 which adjusts the inclination angle of the swash plate 220 with respect to the rotating shaft 210 .
- the inclination adjustment mechanism 400 may include a rotor 410 and a sliding pin 420 .
- the rotor 410 is fastened to the rotating shaft 210 such that the swash plate 220 is fastened to the rotating shaft 210 in such a way to have a variable inclination angle, and rotates together with the rotating shaft 210 .
- the sliding pin 420 connects the swash plate 220 and the rotor 410 .
- the sliding pin 420 is formed in a cylindrical shape.
- a first insertion hole 222 into which the sliding pin 420 is inserted may be formed in the swash plate 220
- a second insertion hole 412 into which the sliding pin 420 is inserted may be formed in the rotor 410 .
- the first insertion hole 222 may be formed in a cylindrical shape such that the sliding pin 420 is rotatable within the first insertion hole 222 .
- the second insertion hole 412 may be formed to extend in one direction such that the sliding pin 420 can move along the second insertion hole 412 .
- a central portion of the sliding pin 420 may be inserted into the first insertion hole 222 , and an end of the sliding pin 420 may be inserted into the second insertion hole 412 .
- the inclination adjustment mechanism 400 may include a first flow path 430 which communicates the discharge chamber S 3 with the crankcase S 4 , and a second flow path 450 which communicates the crankcase S 4 with the suction chamber S 1 .
- the first flow path 430 may be formed to extend from the discharge chamber S 3 to the crankcase S 4 by passing through the rear housing 130 , the valve mechanism 300 , the cylinder block 110 , and the rotating shaft 210 .
- a pressure control valve (not shown) which opens and closes the first flow path 430 may be formed in the first flow path 430 .
- the pressure control valve (not shown) may be formed as a so-called mechanical valve (MCV) or an electronic valve (ECV).
- MCV mechanical valve
- ECV electronic valve
- the pressure control valve (not shown) may be formed to close and open the first flow path 430 , and also to control the opening amount of the first flow path 430 when the first flow path 430 is opened.
- the second flow path 450 may be formed to extend from the crankcase S 4 to the suction chamber S 1 by passing through the cylinder block 110 and the valve mechanism 300 .
- the second flow path 450 has an orifice hole 460 and an orifice control mechanism 470 .
- the orifice hole 460 decompresses a fluid passing through the second flow path 450 in order to prevent the pressure in the suction chamber S 1 from rising.
- the orifice control mechanism 470 controls an effective flow cross-sectional area of the orifice hole 460 so as to prevent the reduction in compressor efficiency due to refrigerant leakage.
- the cross-sectional area of the orifice hole 460 is the area of the orifice hole 460 itself, and the flow cross-sectional area of the orifice hole 460 is the area through which the refrigerant passes in the cross-sectional area of the orifice hole 460 .
- the effective flow cross-sectional area of the orifice hole 460 is the flow cross-sectional area of the orifice hole 460 which becomes a bottleneck among a plurality of orifice holes 460 when the plurality of orifice holes 460 are formed.
- the one orifice hole having a cross-sectional area of 10 mm 2 and there is another orifice hole which is connected in series with the one orifice hole and has a cross-sectional area of 5 mm 2 .
- the cross-sectional area of the one orifice hole is 10 mm 2 and the flow cross-sectional area of the one orifice hole is 2 mm 2
- the cross-sectional area of the other orifice hole is 5 mm 2 and the flow cross-sectional area of the other orifice hole is 3 mm 2 .
- the one orifice hole becomes a bottleneck of all the orifice holes, and the effective flow cross-sectional area of all the orifice holes is 2 mm 2 equal to the flow cross-sectional area of the one orifice hole.
- the orifice hole 460 may include a first orifice hole 462 , a second orifice hole 464 , and a third orifice hole 466 .
- the first orifice hole 462 communicates the crankcase S 4 with a below-described valve chamber 472 and decompresses the refrigerant which is introduced from the crankcase S 4 .
- the second orifice hole 464 communicates the below-described valve chamber 472 with the below-described third orifice hole 466 and decompresses the refrigerant which has passed through the first orifice hole 462 .
- the third orifice hole 466 communicates the second orifice hole 464 with the suction chamber S 1 and decompresses the refrigerant which has passed through the second orifice hole 464 .
- the first orifice hole 462 may be in communication with the below-described valve chamber 472 at a below-described valve chamber first front end surface 472 b such that the first orifice hole 462 can be opened and closed quickly during the reciprocating motion of a below-described valve core 474 and pressure is continuously applied to a bottom surface 4742 ab of a below-described first cylindrical portion.
- the inner diameter of the first orifice hole 462 may be less than the outer diameter of a plurality of protrusions 4742 c to be described later such that a below-described first end 4742 is prevented from escaping from the below-described valve chamber 472 through the first orifice hole 462 .
- the inner diameter of the first orifice hole 462 may be less than the outer diameter of a below-described first cylindrical portion 4742 a such that the first orifice hole 462 is opened and closed by the bottom surface 4742 ab of the below-described first cylindrical portion.
- the second orifice hole 464 may be in communication with the below-described valve chamber 472 at a below-described valve chamber second front end surface 472 c the such that a below-described third cylindrical portion 4744 a can be inserted into the second orifice hole 464 .
- the inner diameter of the second orifice hole 464 may be larger than the outer diameter of the below-described third cylindrical portion 4744 a such that the second orifice hole 464 can decompress the refrigerant in a state where the below-described third cylindrical portion 4744 a has been inserted into the second orifice hole 464 .
- the inner diameter of the second orifice hole 464 may be less than the outer diameter of the plurality of protrusions 4742 c to be described later such that the below-described first end 4742 is prevented from escaping from the below-described valve chamber 472 through the second orifice hole 464 .
- the third orifice hole 466 may be in communication with the second orifice hole 464 at a position facing the below-described valve chamber 472 such that the below-described third cylindrical portion 4744 a can be inserted into the third orifice hole 466 .
- the inner diameter of the third orifice hole 466 may be larger than the outer diameter of the below-described third cylindrical portion 4744 a such that the third orifice hole 466 can decompress the refrigerant in a state where the below-described third cylindrical portion 4744 a has been inserted into the third orifice hole 466 .
- the inner diameter of the third orifice hole 466 may be less than the inner diameter of the second orifice hole 464 such that the opening amount of the third orifice hole 466 is less than the opening amount of the second orifice hole 464 when the below-described third cylindrical portion 4744 a is inserted into both the second orifice hole 464 and the third orifice hole 466 .
- the orifice hole 460 may be formed such that the first orifice hole 462 , the below-described valve chamber 472 , the second orifice hole 464 , and the third orifice hole 466 are sequentially arranged according to the direction of the reciprocating motion of the below-described valve core 474 .
- the orifice control mechanism 470 may include the valve chamber 472 , the valve core 474 , and an elastic member 476 .
- the valve chamber 472 is in communication with the first orifice hole 462 and the second orifice hole 464 .
- the valve core 474 reciprocates along the valve chamber 472 and controls the opening amount of the first orifice hole 462 , the opening amount of the second orifice hole 464 , and the opening amount of the third orifice hole 466 .
- the elastic member 476 applies an elastic force to the valve core 474 .
- the valve chamber 472 may include a valve chamber inner circumferential surface 472 a , the valve chamber first front end surface 472 b , and the valve chamber second front end surface 472 c .
- the valve chamber inner circumferential surface 472 a guides the reciprocating motion of the valve core 474 .
- the valve chamber first front end surface 472 b is located at one end side of the valve chamber inner circumferential surface 472 a .
- the valve chamber second front end surface 472 c is located at the other end side of the valve chamber inner circumferential surface 472 a.
- the valve core 474 may include the first end 4742 and a second end 4744 .
- the first end 4742 reciprocates within the valve chamber 472 and controls the opening amount of the first orifice hole 462 .
- the second end 4744 extends from the first end 4742 and reciprocates together with the first end 4742 , and controls the opening amounts of the second orifice hole 464 and the third orifice hole 466 .
- the first end 4472 may include a first cylindrical portion 4742 a .
- the first cylindrical portion 4742 a includes an outer circumferential surface 4742 aa facing the valve chamber inner circumferential surface 472 a , the bottom surface 4742 ab facing the valve chamber first front end surface 472 b , and an upper surface 4742 ac facing the valve chamber second front end surface 472 c.
- first end 4472 may further include a second cylindrical portion 4742 b .
- the second cylindrical portion 4742 b extends from the upper surface 4742 ac of the first cylindrical portion to the valve chamber second front end surface 472 c side (the second orifice hole 464 side) and forms a concentric circle with the first cylindrical portion 4742 a.
- first end 4472 may further include the plurality of protrusions 4742 c which are formed radially from the outer circumferential surface 4742 aa of the first cylindrical portion and the outer circumferential surface of the second cylindrical portion with respect to the central axes of the first cylindrical portion 4742 a and the second cylindrical portion 4742 b.
- the outer diameter of the plurality of protrusions 4742 c may be formed at an equal level to the inner diameter of the valve chamber 472 , and the length of the plurality of protrusions 4742 c may be less than the length of the valve chamber 472 .
- the length is a value measured along the direction of the reciprocating motion of the valve core 474 .
- the bottom surface 4742 ab of the first cylindrical portion may be formed in parallel with the valve chamber first front end surface 472 b.
- the outer circumferential surface 4742 aa of the first cylindrical portion may be formed apart from the valve chamber inner circumferential surface 472 a . That is, the outer diameter of the first cylindrical portion 4742 a may be less than the outer diameter of the plurality of protrusions 4742 c formed at an equal level to the inner diameter of the valve chamber 472 .
- the outer diameter of the second cylindrical portion 4742 b is formed at an equal level to the outer diameter of the below-described third cylindrical portion 4744 a , so that the outer diameter of the second cylindrical portion 4742 b may be less than the outer diameter of the first cylindrical portion 4742 a and the inner diameter of the second orifice hole 464 .
- a length obtained by adding the length of the first cylindrical portion 4742 a and the length of the second cylindrical portion 4742 b is formed at an equal level to the length of the plurality of protrusions 4742 c , so that the upper surface 4742 ac of the first cylindrical portion may be formed apart from the valve chamber second front end surface 472 c.
- the second end 4744 may include the third cylindrical portion 4744 a which extends from the second cylindrical portion 4742 b to the opposite side of the first cylindrical portion 4742 a (the second orifice hole 464 side) and forms a concentric circle with the second cylindrical portion 4742 b.
- the outer diameter of the third cylindrical portion 4744 a may be less than the inner diameter of the second orifice hole 464 and the inner diameter of the third orifice hole 466 , the length of the third cylindrical portion 4744 a may be greater than the length of the second orifice hole 464 .
- the length of the third cylindrical portion 4744 a may be less than a length obtained by adding the length of the second orifice hole 464 and the length of the third orifice hole 466 .
- a length obtained by adding the length of the third cylindrical portion 4744 a and the length of the plurality of protrusions 4742 c may be greater than the length of the valve chamber 472 .
- a length obtained by adding the length of the third cylindrical portion 4744 a and the length of the plurality of protrusions 4742 c may be less than or equal to the length of the valve chamber 472 .
- the length obtained by adding the length of the third cylindrical portion 4744 a and the length of the plurality of protrusions 4742 c should be greater than the length of the valve chamber 472 .
- the length obtained by adding the length of the third cylindrical portion 4744 a and the length of the plurality of protrusions 4742 c may be less than a length obtained by adding the length of the valve chamber 472 and the length of the second orifice hole 464 .
- the elastic member 476 may be formed of, for example, a compression coil spring to press the valve core 474 toward the valve chamber first front end surface 472 b .
- the compression coil spring is provided in a space between the upper surface 4744 ac of the third cylindrical portion and the basal surface of the third orifice hole 466 .
- the outlet of the third orifice hole 466 may be formed on the inner circumferential surface of the third orifice hole 466 such that the elastic member 476 does not interfere with the flow of the refrigerant passing through the third orifice hole 466 .
- the outlet of the third orifice hole 466 may be formed at a portion of the inner circumferential surface of the third orifice hole 466 , which contacts the basal surface of the third orifice hole 466 in such a way as to always communicate with a space between the upper surface 4744 ac of the third cylindrical portion and the basal surface of the third orifice hole 466 .
- the rear housing 130 includes a post portion 132 which extends from the inner wall surface of the rear housing 130 and is supported by the valve mechanism in order to prevent the deformation of the rear housing 130 .
- the valve chamber 472 , the second orifice hole 464 , and the third orifice hole 466 are formed in the post portion 132 , and the first orifice hole 462 may be formed in the valve mechanism (particularly, a portion of the valve mechanism, which supports the post portion 132 ).
- the rotating shaft 210 and the swash plate 220 may rotate together.
- the piston 230 may reciprocate within the bore 114 by converting the rotational motion of the swash plate 220 into a linear motion.
- the compression chamber communicates with the suction chamber S 1 by the valve mechanism 300 and is shielded from the discharge chamber S 3 , so that the refrigerant in the suction chamber S 1 may be sucked into the compression chamber. That is, when the piston 230 moves from the top dead center to the bottom dead center, the suction valve may open the suction port and the discharge valve may close the discharge port, and then, the refrigerant in the suction chamber S 1 may be sucked into the compression chamber through the suction hole and the suction port.
- the compression chamber is shielded from the suction chamber S 1 and the discharge chamber S 3 by the valve mechanism 300 , and the refrigerant in the compression chamber may be compressed. That is, when the piston 230 moves from the bottom dead center to the top dead center, the suction valve may close the suction port and the discharge valve may close the discharge port, and then the refrigerant in the compression chamber may be compressed.
- the compression chamber is shielded from the suction chamber S 1 by the valve mechanism 300 and communicates with the discharge chamber S 3 , so that the refrigerant compressed in the compression chamber may be discharged to the discharge chamber S 3 . That is, when the piston 230 reaches the top dead center, the suction valve may close the suction port and the discharge valve may open the discharge port, and then the refrigerant compressed in the compression chamber may be discharged to the discharge chamber S 3 through the discharge hole and the discharge port.
- the refrigerant discharge amount may be controlled as follows.
- the compressor when the compressor is stopped, the compressor is set to a minimum mode in which the refrigerant discharge amount is minimum. That is, the swash plate 220 is disposed close to perpendicular to the rotating shaft 210 , an inclination angle of the swash plate 220 may be close to zero.
- the inclination angle of the swash plate 220 may be measured as an angle between the rotating shaft 210 of the swash plate 220 and a normal of the swash plate 220 , based on the center of rotation of the swash plate 220 .
- the compressor is adjusted to a maximum mode in which the refrigerant discharge amount is maximum. That is, the first flow path 430 may be closed by the pressure control valve (not shown) and the pressure in the crankcase S 4 may be reduced to the level of the suction pressure. That is, a differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 may be reduced to the minimum degree. Accordingly, the pressure in the crankcase S 4 applied to the piston 230 is reduced to the minimum degree, and the stroke of the piston 230 is increased to the maximum degree. Then, the inclination angle of the swash plate 220 is increased to the maximum degree, and the refrigerant discharge amount is increased to the maximum degree.
- the opening amount of the first flow path 430 may be controlled by the pressure control valve (not shown), so that the pressure in the crankcase S 4 may be controlled. That is, the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 may be controlled. Accordingly, the pressure in the crankcase S 4 applied to the piston 230 is controlled, so that the stroke of the piston 230 may be adjusted, the inclination angle of the swash plate 220 may be adjusted, and the refrigerant discharge amount may be adjusted.
- the first flow path 430 is opened by the pressure control valve (not shown), and the opening amount of the first flow path 430 is increased by the pressure control valve (not shown), so that the pressure in the crankcase S 4 may be increased. That is, the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 may be increased. Accordingly, the pressure in the crankcase S 4 applied to the piston 230 is increased, so that the stroke of the piston 230 may be reduced, the inclination angle of the swash plate 220 may be reduced, and the refrigerant discharge amount may be reduced.
- the first flow path 430 is opened by the pressure control valve (not shown), and the opening amount of the first flow path 430 is decreased by the pressure control valve (not shown), so that the pressure in the crankcase S 4 may be decreased. That is, the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 may be reduced. Accordingly, the pressure in the crankcase S 4 applied to the piston 230 is decreased, so that the stroke of the piston 230 may be increased, the inclination angle of the swash plate 220 may be increased, and the refrigerant discharge amount may be increased.
- the amount of refrigerant which is introduced into the crankcase S 4 from the discharge chamber S 3 must be reduced by closing the first flow path 430 or by reducing the opening amount of the first flow path 430 . Also, at the same time, the refrigerant in the crankcase S 4 must be discharged to the outside of the crankcase S 4 .
- the second flow path 450 which guides the refrigerant in the crankcase S 4 to the suction chamber S 1 and the orifice hole 460 which decompresses the refrigerant passing through the second flow path 450 so as to prevent the pressure in the suction chamber S 1 from rising.
- the effective flow cross-sectional area of the orifice hole 460 is formed to have a constant large area
- the pressure in the crankcase S 4 the differential pressure between the pressure in the crankcase and the pressure in the suction chamber
- the refrigerant in the crankcase S 4 can be quickly discharged to the suction chamber S 1 , and thus, it is advantageous in terms of responsiveness.
- the pressure in the crankcase S 4 should be maintained or increased, the refrigerant in the crankcase S 4 unnecessarily leaks into the suction chamber S 1 , and thus, it may be disadvantageous in terms of efficiency.
- the pressure in the crankcase S 4 (the differential pressure between the pressure in the crankcase and the pressure in the suction chamber) should be maintained or increased, the amount of the refrigerant which leaks from the crankcase S 4 to the suction chamber S 1 is reduced, and thus, it is advantageous in terms of efficiency.
- the pressure in the crankcase S 4 (the differential pressure between the pressure in the crankcase and the pressure in the suction chamber) should be reduced, it is difficult for the refrigerant in the crankcase S 4 to be discharged to the suction chamber S 1 , and thus, it may be disadvantageous in terms of responsiveness.
- the first orifice hole 462 , the valve chamber 472 , the second orifice hole 464 , and the third orifice hole 466 may be formed sequentially according to the direction of the reciprocating motion of the valve core 474 .
- the first end 4742 may be formed to be able to reciprocate within the valve chamber 472
- the second end 4744 may be formed to be able to reciprocate together with the first end 4742 with the insertion into the second orifice hole 464 and may be formed to be able to enter and exit the third orifice hole 466 .
- the inner diameter of the third orifice hole 466 may be formed to be less than the inner diameter of the second orifice hole 464
- the outer diameter of the third cylindrical portion 4744 a may be formed to be less than the inner diameter of the third orifice hole 466 , so that an area obtained by subtracting the area of the third cylindrical portion 4744 a from the cross-sectional area of the second orifice hole 464 is formed as a first predetermined area A 1
- an area obtained by subtracting the area of the third cylindrical portion 4744 a from the cross-sectional area of the third orifice hole 466 may be formed as a second area A 2 greater than zero and less than the first area A 1 .
- the cross-sectional area of the first orifice hole 462 may be formed at an equal level to the first area A 1 . Also, an area obtained by subtracting the area of the first cylindrical portion 4742 a and the area of the plurality of protrusions 4742 c from the cross-sectional area of the valve chamber 472 may be formed to be equal to or greater than the cross-sectional area of the first orifice hole 462 such that the refrigerant which has passed through the first orifice hole 462 can flow smoothly toward the second orifice hole.
- the area obtained by subtracting the area of the first cylindrical portion 4742 a and the area of the plurality of protrusions 4742 c from the cross-sectional area of the valve chamber 472 may be formed to be equal to or greater than the first area A 1 .
- the first area A 1 may be formed to the maximum degree within a range that sufficiently decompresses the refrigerant passing through the second flow path 450 and may be formed to be less than the cross-sectional area of the third orifice hole 466 .
- the opening amount of the first orifice hole 462 is controlled by the first end 4742
- the opening amount of the second orifice hole 464 and the opening amount of the third orifice hole 466 are controlled by the second end 4744
- the effective flow cross-sectional area of the orifice hole 460 may be formed to change according to the pressure in the crankcase S 4 (the differential pressure between the pressure in the crankcase and the pressure in the suction chamber).
- the valve chamber 472 , the inner diameter of the second orifice hole 464 , and the inner diameter of the third orifice hole 466 are formed to be larger than the outer diameter of the third cylindrical portion 4744 a , the valve chamber 472 , the second orifice hole 464 and the third orifice hole 466 may always be in communication with the suction chamber S 1 regardless of the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 (regardless of the position of the valve core 474 ).
- a force applied to one side of the valve core 474 (a value obtained through multiplication of the pressure which passes through the first orifice hole 462 from the crankcase S 4 and is applied to the bottom surface 4742 ab of the first cylindrical portion and a pressure application area thereof) may be equal to or less than a force applied to the other side of the valve core 474 (a force obtained by adding a force applied by the elastic member 476 and a value obtained through multiplication of the pressure applied to the upper surface 4742 ac of the first cylindrical portion, to an upper surface 4742 cc of the plurality of protrusions, and to the upper surface 4744 ac of the third cylindrical portion and a pressure application area thereof).
- valve core 474 moves toward the valve chamber first front end surface 472 b , so that the bottom surface 4742 ab of the first cylindrical portion comes in contact with the valve chamber first front end surface 472 b .
- the first orifice hole 462 may be closed by the valve core 474 .
- the flow cross-sectional area of the first orifice hole 462 may be zero.
- the first orifice hole 462 becomes a bottleneck of the orifice hole 460
- the effective flow cross-sectional area of the orifice hole 460 may be, as shown in FIG. 8 , zero that is the flow cross-sectional area of the first orifice hole 462 .
- the force applied to one side of the valve core 474 may be greater than the force applied to the other side of the valve core 474 .
- valve core 474 moves toward the valve chamber second front end surface 472 c , so that the bottom surface 4742 ab of the first cylindrical portion may be spaced apart from the valve chamber first front end surface 472 b and the first orifice hole 462 may be opened.
- the refrigerant in the crankcase S 4 may flow toward the suction chamber S 1 . That is, the refrigerant in the crankcase S 4 may pass through the first orifice hole 462 and may be introduced into a space between the valve chamber first front end surface 472 b and first end 4742 . Also, the refrigerant in the space between the valve chamber first front end surface 472 b and first end 4742 may be introduced into a space between the valve chamber inner circumferential surface 472 a and the outer circumferential surface 4742 aa of the first cylindrical portion.
- the refrigerant in the space between the valve chamber inner circumferential surface 472 a and the outer circumferential surface 4742 aa of the first cylindrical portion may be introduced into a space between the valve chamber inner circumferential surface 472 a and the outer circumferential surface of the second cylindrical portion.
- the refrigerant in the space between the valve chamber inner circumferential surface 472 a and the outer circumferential surface of the second cylindrical portion may be introduced into a space between the valve chamber inner circumferential surface 472 a and the outer circumferential surface of the third cylindrical portion.
- the refrigerant in the space between the valve chamber inner circumferential surface 472 a and the outer circumferential surface of the third cylindrical portion may be introduced into a space between the inner circumferential surface of the second orifice hole 464 and the outer circumferential surface of the third cylindrical portion.
- the refrigerant in the space between the inner circumferential surface of the second orifice hole 464 and the outer circumferential surface of the third cylindrical portion may be introduced into the third orifice hole 466 .
- the refrigerant of the third orifice hole 466 may be discharged to the suction chamber S 1 through the outlet of the third orifice hole 466 .
- the flow cross-sectional area of the first orifice hole 462 may be the first area A 1 equal to the cross-sectional area of the first orifice hole 462 .
- the flow cross-sectional area of the second orifice hole 464 may be the first area A 1 which is less than the cross-sectional area of the second orifice hole 464 .
- the flow cross-sectional area of the third orifice hole 466 may be equal to the cross-sectional area of the third orifice hole 466 . That is, the flow cross-sectional area of the third orifice hole 466 may be greater than the second area A 2 and even greater than the first area A 1 .
- the effective flow cross-sectional area of the orifice hole 460 may be, as shown in FIG. 8 , the first area A 1 which is both the flow cross-sectional area of the second orifice hole 464 and the flow cross-sectional area of the first orifice hole 462 .
- the force applied to one side of the valve core 474 may be greater than the force applied to the other side of the valve core 474 .
- valve core 474 moves toward the valve chamber second front end surface 472 c , so that the bottom surface 4742 ab of the first cylindrical portion may be further spaced apart from the valve chamber first front end surface 472 b and the first orifice hole 462 may continue to be opened.
- the refrigerant in the crankcase S 4 may continue to flow toward the suction chamber S 1 . That is, the refrigerant in the crankcase S 4 may pass through the first orifice hole 462 and may be introduced into a space between the valve chamber first front end surface 472 b and first end 4742 . Also, the refrigerant in the space between the valve chamber first front end surface 472 b and first end 4742 may be introduced into a space between the valve chamber inner circumferential surface 472 a and the outer circumferential surface 4742 aa of the first cylindrical portion.
- the refrigerant in the space between the valve chamber inner circumferential surface 472 a and the outer circumferential surface 4742 aa of the first cylindrical portion may be introduced into a space between the valve chamber inner circumferential surface 472 a and the outer circumferential surface of the second cylindrical portion.
- the refrigerant in the space between the valve chamber inner circumferential surface 472 a and the outer circumferential surface of the second cylindrical portion may be introduced into a space between the inner circumferential surface of the second orifice hole 464 and the outer circumferential surface of the third cylindrical portion.
- the refrigerant in the space between the valve chamber inner circumferential surface 472 a and the outer circumferential surface 4742 aa of the first cylindrical portion may be introduced into the space between the inner circumferential surface of the second orifice hole 464 and the outer circumferential surface of the third cylindrical portion by the second cylindrical portion 4742 b .
- the refrigerant in the space between the inner circumferential surface of the second orifice hole 464 and the outer circumferential surface of the third cylindrical portion may be introduced into a space between the inner circumferential surface of the third orifice hole 466 and the outer circumferential surface of the third cylindrical portion. Also, the refrigerant in the space between the inner circumferential surface of the third orifice hole 466 and the outer circumferential surface of the third cylindrical portion may be discharged to the suction chamber S 1 through the outlet of the third orifice hole 466 .
- the flow cross-sectional area of the first orifice hole 462 may be still the first area A 1 equal to the cross-sectional area of the first orifice hole 462 .
- the flow cross-sectional area of the second orifice hole 464 may be still the first area A 1 which is less than the cross-sectional area of the second orifice hole 464 .
- the flow cross-sectional area of the third orifice hole 466 may be the second area A 2 that is less than the cross-sectional area of the third orifice hole 466 and less than the first area A 1 .
- the effective flow cross-sectional area of the orifice hole 460 may be, as shown in FIG. 8 , the second area A 2 which is the flow cross-sectional area of the third orifice hole 466 .
- the effective flow cross-sectional area of the orifice hole 460 is variable by the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 (more precisely, the pressure in the crankcase S 4 ). Therefore, when the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 (more precisely, the pressure in the crankcase S 4 ) should be maintained or increased, the amount of the refrigerant which leaks from the crankcase S 4 to the suction chamber S 1 may be reduced. That is, referring to FIG.
- the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 is in a range less than the first pressure P 1 and in a range equal to or greater than the second pressure P 2 , the effective flow cross-sectional area of the orifice hole 460 may be reduced than the first area A 1 .
- the amount of refrigerant which leaks from the crankcase S 4 to the suction chamber S 1 may be reduced as much as an oblique-lined part in FIG. 8 .
- the amount of the refrigerant which is introduced from the discharge chamber S 3 into the crankcase S 4 through the first flow path 430 may be reduced, and the amount of the refrigerant which is discharged from the discharge chamber S 3 through the refrigerant discharge pipe (not shown) in a cooling cycle may be relatively increased. Accordingly, even if the compressor does relatively little work (compress), it is possible to easily achieve a desired cooling or heating level, so that the power required to drive the compressor is reduced, and compressor efficiency can be improved.
- the refrigerant in the crankcase S 4 can be rapidly discharged to the suction chamber S 1 , so that the responsiveness can be improved. That is, the refrigerant discharge amount can be quickly controlled.
- the time required to switch to the maximum mode may be reduced. That is, in switching to the maximum mode, when the refrigerant in the crankcase S 4 is smoothly discharged to the suction chamber S 1 side even if the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 is gradually reduced to a level close to zero, the time required to switch to the maximum mode can be reduced.
- the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 becomes less than the second pressure P 2 and is reduced to a level close to zero, the effective flow cross-sectional area of the orifice hole 460 is reduced, so that the refrigerant in the crankcase S 4 cannot be smoothly discharged to the suction chamber S 1 side. Accordingly, the time required to switch to the maximum mode may be increased.
- the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 becomes less than the second pressure P 2 and is reduced to a level close to zero, the effective flow cross-sectional area of the orifice hole 460 is increased, so that the refrigerant in the crankcase S 4 can be smoothly discharged to the suction chamber S 1 side. Accordingly, the time required to switch to the maximum mode may be reduced.
- a vehicle cooling system includes a vapor compression refrigeration cycle mechanism.
- the vapor compression refrigeration cycle mechanism includes not only a compressor that compresses a low-temperature and low-pressure gaseous refrigerant into a high-temperature and high-pressure gaseous refrigerant but also a condenser that condenses the high-temperature and high-pressure gaseous refrigerant discharged from the compressor into a low-temperature and high-pressure liquid refrigerant, an expansion valve that expands the low-temperature and high-pressure liquid refrigerant discharged from the condenser into a low-temperature and low-pressure liquid refrigerant, and an evaporator that evaporates the low-temperature and low-pressure liquid refrigerant discharged from the expansion valve into a low-temperature and low-pressure gaseous refrigerant.
- the compressor when a start signal is input, the compressor is driven to compress the refrigerant, and the refrigerant discharged from the compressor is circulated through the condenser, the expansion valve, and the evaporator and is collected to the compressor.
- the condenser and the evaporator perform heat-exchange with air, and a portion of the air heat-exchanged with the condenser and the evaporator is supplied to the passenger room of the vehicle. Also, cooling, heating, and dehumidification are provided.
- the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 becomes zero and less than the first pressure P 1 .
- the first orifice hole 462 is closed by the valve core 474 , so that the effective flow cross-sectional area of the orifice hole 460 may be zero.
- the refrigerant and the oil cannot move between the crankcase S 4 and the suction chamber S 1 , the refrigerant and the oil within the compressor can be prevented from moving to the outside of the compressor. Accordingly, the amount of oil within the compressor can be prevented from being less than a predetermined reference amount of oil, and damage to the compressor due to deficient oil can be prevented.
- the elastic member 476 in order to ensure the reliability of the behavior of the valve core 474 when the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 is reduced, the elastic member 476 is provided, and the elastic member 476 is formed to have a high modulus of elasticity.
- the elastic member is not limited thereto, and as shown in FIGS. 9 and 10 , in order to advance the opening time of the orifice hole 460 , the elastic member 476 may be formed to have a low modulus of elasticity.
- the effective flow cross-sectional area of the orifice hole 460 may become the first area A 1 in a range in which the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 is equal to or greater than the first new pressure P 1 ′ and is less than the second new pressure P 2 ′.
- the elastic member 476 is mainly intended to return the valve core 474 to of the valve chamber first front end surface 472 b side. Therefore, it may be desirable to improve the responsiveness by the fact that, when the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 becomes close to zero, the modulus of elasticity of the elastic member 476 should be as less as possible within a range in which the valve core 474 can be moved to the valve chamber first front end surface 472 b side.
- the cross-sectional area of the first orifice hole 462 is formed at an equal level to the first area A 1 , but is not limited thereto.
- the cross-sectional area of the first orifice hole 462 may be formed larger than the first area A 1 .
- the effective flow cross-sectional area when the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 is less than the first pressure P 1 , the effective flow cross-sectional area may be formed to become zero, and when the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 is equal to or greater than the first pressure P 1 and less than the second pressure P 2 , the effective flow cross-sectional area may be formed to be the first area A 1 , and when the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 is equal to or greater than the second pressure P 2 , the effective flow cross-sectional area may be formed to be the second area A 2 .
- the effective flow cross-sectional area when the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 is less than the first pressure P 1 , the effective flow cross-sectional area may be formed to become zero, when the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 is equal to or greater than the first pressure P 1 and less than the second pressure P 2 , the effective flow cross-sectional area may be formed to be greater than zero and less than the first area A 1 , when the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 is equal to or greater than the first pressure P 2 and less than a third pressure, the effective flow cross-sectional area may be formed to be the first area A 1 , when the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 is equal to or greater than the third pressure and less than a fourth pressure, the effective flow cross-sectional area may be formed to be less than the first area A 1 and
- the effective flow cross-sectional area of the orifice hole 460 may be increased linearly in proportion to the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 . Also, in a range in which the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 is greater than or equal to the third pressure and less than the fourth pressure, the effective flow cross-sectional area of the orifice hole 460 may be decreased linearly in proportion to the differential pressure between the pressure in the crankcase S 4 and the pressure in the suction chamber S 1 .
- the present disclosure provides a variable displacement swash plate type compressor capable of adjusting an inclination angle of a swash plate by controlling a pressure of a crankcase equipped with a swash plate.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Compressor (AREA)
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KR10-2018-0084072 | 2018-07-19 | ||
KR1020180084072A KR102547593B1 (ko) | 2018-07-19 | 2018-07-19 | 가변 용량 사판식 압축기 |
PCT/KR2019/008921 WO2020017917A1 (ko) | 2018-07-19 | 2019-07-19 | 가변 용량 사판식 압축기 |
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US20210140419A1 US20210140419A1 (en) | 2021-05-13 |
US11286919B2 true US11286919B2 (en) | 2022-03-29 |
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US16/979,273 Active US11286919B2 (en) | 2018-07-19 | 2019-07-19 | Variable displacement swash plate type compressor |
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US (1) | US11286919B2 (ko) |
JP (1) | JP6972364B2 (ko) |
KR (1) | KR102547593B1 (ko) |
CN (1) | CN111656012B (ko) |
DE (1) | DE112019003639T5 (ko) |
WO (1) | WO2020017917A1 (ko) |
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KR20210146716A (ko) * | 2020-05-27 | 2021-12-06 | 한온시스템 주식회사 | 사판식 압축기 |
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EP3236068A4 (en) * | 2014-12-18 | 2018-06-06 | Valeo Japan Co., Ltd. | Variable capacity compressor |
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2018
- 2018-07-19 KR KR1020180084072A patent/KR102547593B1/ko active IP Right Grant
-
2019
- 2019-07-19 CN CN201980009979.XA patent/CN111656012B/zh active Active
- 2019-07-19 WO PCT/KR2019/008921 patent/WO2020017917A1/ko active Application Filing
- 2019-07-19 JP JP2020542245A patent/JP6972364B2/ja active Active
- 2019-07-19 DE DE112019003639.4T patent/DE112019003639T5/de active Pending
- 2019-07-19 US US16/979,273 patent/US11286919B2/en active Active
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US3503417A (en) * | 1967-08-07 | 1970-03-31 | Toyota Motor Co Ltd | Control valve for regulating flow of blow-by gas |
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US20040120829A1 (en) | 2002-12-23 | 2004-06-24 | Pitla Srinivas S. | Controls for variable displacement compressor |
WO2004061304A1 (ja) | 2002-12-27 | 2004-07-22 | Zexel Valeo Climate Control Corporation | 可変容量型圧縮機の制御装置 |
US8869826B2 (en) * | 2009-05-21 | 2014-10-28 | Debiotech S.A. | Passive fluid flow regulator |
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Also Published As
Publication number | Publication date |
---|---|
KR102547593B1 (ko) | 2023-06-27 |
JP2021513022A (ja) | 2021-05-20 |
KR20200009554A (ko) | 2020-01-30 |
CN111656012A (zh) | 2020-09-11 |
US20210140419A1 (en) | 2021-05-13 |
JP6972364B2 (ja) | 2021-11-24 |
CN111656012B (zh) | 2022-03-29 |
WO2020017917A1 (ko) | 2020-01-23 |
DE112019003639T5 (de) | 2021-04-08 |
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